EP2824334A1 - Entraînement linéaire hydraulique - Google Patents

Entraînement linéaire hydraulique Download PDF

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Publication number
EP2824334A1
EP2824334A1 EP13175605.8A EP13175605A EP2824334A1 EP 2824334 A1 EP2824334 A1 EP 2824334A1 EP 13175605 A EP13175605 A EP 13175605A EP 2824334 A1 EP2824334 A1 EP 2824334A1
Authority
EP
European Patent Office
Prior art keywords
hydraulic
pressure
chamber
linear drive
hydraulic machine
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP13175605.8A
Other languages
German (de)
English (en)
Inventor
Ingo Geier
Klaus Oberndorfer
Stephan Schäufele
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Siemens AG
Original Assignee
Siemens AG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Siemens AG filed Critical Siemens AG
Priority to EP13175605.8A priority Critical patent/EP2824334A1/fr
Publication of EP2824334A1 publication Critical patent/EP2824334A1/fr
Withdrawn legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
    • F15B11/17—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors using two or more pumps
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B29—WORKING OF PLASTICS; WORKING OF SUBSTANCES IN A PLASTIC STATE IN GENERAL
    • B29C—SHAPING OR JOINING OF PLASTICS; SHAPING OF MATERIAL IN A PLASTIC STATE, NOT OTHERWISE PROVIDED FOR; AFTER-TREATMENT OF THE SHAPED PRODUCTS, e.g. REPAIRING
    • B29C45/00—Injection moulding, i.e. forcing the required volume of moulding material through a nozzle into a closed mould; Apparatus therefor
    • B29C45/17—Component parts, details or accessories; Auxiliary operations
    • B29C45/76—Measuring, controlling or regulating
    • B29C45/82—Hydraulic or pneumatic circuits
    • B29C2045/828—Bidirectional pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/2053—Type of pump
    • F15B2211/20561—Type of pump reversible
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/2053—Type of pump
    • F15B2211/20569—Type of pump capable of working as pump and motor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/20576—Systems with pumps with multiple pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/63—Electronic controllers
    • F15B2211/6303—Electronic controllers using input signals
    • F15B2211/6336—Electronic controllers using input signals representing a state of the output member, e.g. position, speed or acceleration
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/705—Output members, e.g. hydraulic motors or cylinders or control therefor characterised by the type of output members or actuators
    • F15B2211/7051—Linear output members
    • F15B2211/7053—Double-acting output members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B7/00—Systems in which the movement produced is definitely related to the output of a volumetric pump; Telemotors
    • F15B7/005—With rotary or crank input
    • F15B7/006—Rotary pump input

Definitions

  • the invention relates to a hydraulic linear drive with a running with at least two oppositely acting pressure chambers hydraulic cylinder.
  • the two pressure chambers of the at least two pressure chambers of the hydraulic cylinder are referred to below for distinction as the first pressure chamber and second pressure chamber or as a pressure chamber and counter chamber.
  • Hydraulic linear drives are known per se and are used, for example, in hydraulic injection molding machines or hydraulic presses for moving a press ram or for moving an upper mold.
  • a pressure medium that is normally a hydraulic medium, usually hydraulic oil, fed to a proportional valve, which is connected with its outputs to the two pressure chambers of the hydraulic cylinder.
  • a proportional valve which is connected with its outputs to the two pressure chambers of the hydraulic cylinder.
  • the hydraulic medium is pressed into one of the pressure chambers of the hydraulic cylinder.
  • the amount of oil flowing in or out is influenced by the position of the proportional valve.
  • the displaced during a feed from the opposite chamber oil flows through the proportional valve back into a functioning as a pressure medium reservoir tank.
  • a hydraulic machine must provide a pressure that is sufficient to overcome a force acting on the piston rod of the hydraulic linear drive process force. Only so is a controllability / controllability of the oil flow and thus a controllability / controllability of the piston movement guaranteed.
  • the resulting Throttling losses in the proportional valve however, often exceed 50% of the power fed in by the hydromachine. This is disadvantageous and with the constant increase in the cost of energy is trying to avoid such energy losses as far as possible.
  • An object of the present invention starting from this prior art is to provide a further embodiment of a hydraulic linear drive.
  • a hydraulic linear drive with the features of claim 1.
  • a hydraulic linear drive with a with at least two oppositely acting pressure chambers - first pressure chamber and second pressure chamber or pressure chamber and counter chamber - running hydraulic cylinder and with a first and a second hydraulic machine for pressure medium supply of the two pressure chambers, wherein the first hydraulic machine for pressure medium supply to the first Pressure chamber is coupled, provided that the second hydraulic machine for pressure medium exchange to the first pressure chamber and the hydraulically opposed second pressure chamber (counter chamber) is coupled.
  • the advantage of the invention is not only that in this solution, a proportional valve and the concomitant throttle losses are avoided, but also in that the second hydraulic machine can support the first hydraulic machine, so that the capacity of the first hydraulic machine compared to a situation , at each a hydraulic machine works in exactly one pressure chamber of the hydraulic cylinder, can be reduced.
  • the hydraulic cylinder is a differential cylinder with a piston chamber and an annular chamber as the two of the hydraulic cylinder and oppositely acting pressure chambers.
  • the first pressure chamber, to which the first hydraulic machine is coupled to the pressure medium supply, the piston chamber of the hydraulic cylinder and the second pressure chamber corresponding to the annular chamber of the hydraulic cylinder, the second hydraulic machine is coupled to the pressure medium supply to the piston chamber and to the annular chamber
  • the selection as to whether the first hydraulic machine is coupled to the first pressure chamber / piston chamber or to the second pressure chamber / annular chamber depends on the respective application situation.
  • An advantage of the solution described here is thus also that in this respect a previously non-existent flexibility, because in a hydraulic linear drive, in which the first hydraulic machine is connected to the piston chamber, is a major problem the first hydraulic machine to the second pressure chamber / annular chamber or vice versa possible.
  • first and second hydraulic machine is in principle known per se in each case a constant displacement pump with a variable speed electric motor, but also a group of multiple constant pumps, each with a variable speed electric motor into consideration.
  • a variable displacement pump with a variable speed or a fixed speed electric motor or a group of such units is considered.
  • a position of the linear drive is detected in a suitable manner and the position thus detected is used as the basis for a control or position control of the linear drive.
  • a position measuring system for detecting a position of the linear drive is provided for a position control even with such a hydraulic linear drive, so that by means of a position controller, a control of the first and / or second hydraulic machine corresponding to the detected position and a predetermined position setpoint occurs.
  • FIG. 1 shows a known hydraulic linear drive 10.
  • This comprises a hydraulic cylinder 12 in the form of a differential pressure cylinder with two oppositely acting pressure chambers 14, 16, namely a first pressure chamber 14 which is here and hereinafter referred to as piston chamber 14 in the interests of better readability of the description, and a second pressure chamber 16, which is hereinafter and hereinafter referred to as annular chamber 16 and for distinction.
  • a pressure medium namely usually hydraulic oil
  • a pressure medium namely usually hydraulic oil
  • the pressure medium which is often referred to as oil or hydraulic oil in the following without dispensing with further generality, passes either into the piston chamber 14 or into the annular chamber 16 from the pressure medium reservoir 30 respective counter chamber 14, 16 displaced oil flows through the proportional valve 22 back into the pressure medium reservoir 30, so for example an oil tank.
  • FIG. 2 shows a likewise known embodiment of a hydraulic linear drive 10, which seeks to avoid losses associated with the use of a proportional valve 22.
  • the illustrated hydraulic linear drive 10 is characterized by that in addition to the previously ( FIG. 1 ) required hydraulic machine 24, which is hereinafter referred to as the first hydraulic machine 24, a further hydraulic machine, that is, a second hydraulic machine 32, is provided.
  • Both hydraulic machines 24, 32 each include a pump 26 and an electric motor 28 provided for driving the pump 26.
  • Both hydraulic machines 24, 32 operate from a pressure medium reservoir 30 or a common pressure medium reservoir 30.
  • the first hydraulic machine 24 is coupled to the piston chamber 14 of the hydraulic cylinder 12
  • the second hydraulic machine 32 is coupled to the counter chamber to the piston chamber 14, that is, to the annular chamber 16 of the hydraulic cylinder 12.
  • To adjust the position of the piston 18 and thus to adjust a position of one end of the piston 18 emanating from the piston rod 20 is a position-controlled control of either the first hydraulic machine 24 or the second hydraulic machine 32 or both hydraulic machines 24, 32, wherein for a forward stroke of the piston 18th the first hydraulic machine 24 pressure medium, ie in particular oil, promotes / presses in the piston chamber 14 and then due to the then from the Annular chamber 16 displaced oil, the second hydraulic machine 32 is operated as a generator.
  • FIG. 3 shows a schematically simplified embodiment of a hydraulic linear drive 10 according to the invention.
  • the explanation also takes place, however, without waiving any further generality, based on a hydraulic cylinder 12 in the form of a differential cylinder.
  • the approach is just as suitable for a hydraulic linear drive 10 with a hydraulic cylinder 12 in the form of a Gleichgangzylinders.
  • a first and a second hydraulic machine 24, 32 are provided.
  • the first hydraulic machine 24 is coupled to one of the two pressure chambers 14, 16, here to the piston chamber 14.
  • the hydraulic linear drive 10 promotes / presses the first hydraulic motor 24 for a forward stroke of the piston 18 pressure medium, so for example hydraulic oil, from a pressure medium reservoir 30 into the respective pressure chamber 14, 16 and in a return stroke, the respective pressure fluid flows through the then regeneratively operated first hydraulic machine 24 comprised pump 26 back to the pressure medium reservoir 30.
  • the second hydraulic machine 32 is not equipped with a pressure medium reservoir 30 (FIG. FIG. 2 ) connected.
  • the second hydrant 32 is coupled to both the first pressure chamber 14 and the second pressure chamber 16 for fluid communication.
  • the second hydraulic machine 32 conveys pressure fluid from the piston chamber 14 (first pressure chamber) into the annular chamber 16 (second pressure chamber). From the piston chamber 14 (first pressure chamber) thereby displaced pressure medium flows via the pump 26 of the first hydraulic machine 24, which is operated as a generator, back into the pressure medium reservoir 30th
  • the second hydraulic machine 32 supports the first hydraulic machine 24 depending on the direction of movement of the piston 18.
  • A an area ratio of the first pressure chamber 14 symbolically indicated by A to the second pressure chamber 16
  • the piston rod 20 moving with the piston 18 reduces the delivery rate of the first hydraulic machine by a factor of 1 / (1 + (1 / A)) can be.
  • the required capacity of the first hydraulic machine is reduced by 25%.
  • the pumps 26 of the two hydraulic machines 24, 32 are for example constant pumps. Otherwise also so-called variable displacement pumps come into consideration.
  • the motors 28 of the two hydraulic machines 24, 32 are, for example, variable-speed electric motors. In a variable displacement pump is in principle also a speed-resistant electric motor into consideration.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Pressure Circuits (AREA)
EP13175605.8A 2013-07-08 2013-07-08 Entraînement linéaire hydraulique Withdrawn EP2824334A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP13175605.8A EP2824334A1 (fr) 2013-07-08 2013-07-08 Entraînement linéaire hydraulique

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP13175605.8A EP2824334A1 (fr) 2013-07-08 2013-07-08 Entraînement linéaire hydraulique

Publications (1)

Publication Number Publication Date
EP2824334A1 true EP2824334A1 (fr) 2015-01-14

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EP13175605.8A Withdrawn EP2824334A1 (fr) 2013-07-08 2013-07-08 Entraînement linéaire hydraulique

Country Status (1)

Country Link
EP (1) EP2824334A1 (fr)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2020083483A1 (fr) * 2018-10-24 2020-04-30 Volvo Construction Equipment Ab Procédé de commande d'un système hydraulique d'une machine de travail
WO2020083482A1 (fr) * 2018-10-24 2020-04-30 Volvo Construction Equipment Ab Système hydraulique pour machine de travail
WO2020216453A1 (fr) * 2019-04-26 2020-10-29 Volvo Construction Equipment Ab Système hydraulique et procédé permettant de commander un système hydraulique d'un engin de chantier
WO2022122934A1 (fr) * 2020-12-09 2022-06-16 Liebherr-Werk Biberach Gmbh Engin de levage et procédé pour régler la flèche d'un tel engin de levage

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19600650A1 (de) 1996-01-10 1997-07-24 Trinova Gmbh Antrieb für einen hydraulischen doppelwirkenden Aktuator
DE102008039011A1 (de) 2008-08-21 2010-02-25 MAE Maschinen- und Apparatebau Götzen GmbH & Co. KG Druckspeicherlose hydraulische Antriebsanordnung sowie Verfahren zum druckspeicherlosen hydraulischen Antreiben eines Verbrauchers
US20120055149A1 (en) * 2010-09-02 2012-03-08 Bucyrus International, Inc. Semi-closed hydraulic systems
WO2012055579A1 (fr) * 2010-10-27 2012-05-03 Coskunöz Metal Form Makina Endüstri Ve Tic. A.S. Presse servo-hydraulique

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19600650A1 (de) 1996-01-10 1997-07-24 Trinova Gmbh Antrieb für einen hydraulischen doppelwirkenden Aktuator
DE102008039011A1 (de) 2008-08-21 2010-02-25 MAE Maschinen- und Apparatebau Götzen GmbH & Co. KG Druckspeicherlose hydraulische Antriebsanordnung sowie Verfahren zum druckspeicherlosen hydraulischen Antreiben eines Verbrauchers
US20120055149A1 (en) * 2010-09-02 2012-03-08 Bucyrus International, Inc. Semi-closed hydraulic systems
WO2012055579A1 (fr) * 2010-10-27 2012-05-03 Coskunöz Metal Form Makina Endüstri Ve Tic. A.S. Presse servo-hydraulique

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
JOHNSON J L: "SUMMARIZING TWO-PUMP CONTROL", HYDRAULICS AND PNEUMATICS, PENTON MEDIA, CLEVELAND, OH, US, vol. 60, no. 6, 1 June 2007 (2007-06-01), pages 22,24,27, XP001506059, ISSN: 0018-814X *

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2020083483A1 (fr) * 2018-10-24 2020-04-30 Volvo Construction Equipment Ab Procédé de commande d'un système hydraulique d'une machine de travail
WO2020083482A1 (fr) * 2018-10-24 2020-04-30 Volvo Construction Equipment Ab Système hydraulique pour machine de travail
CN112955667A (zh) * 2018-10-24 2021-06-11 沃尔沃建筑设备公司 用于控制作业机械的液压系统的方法
US11459732B2 (en) 2018-10-24 2022-10-04 Volvo Construction Equipment Ab Hydraulic system for a working machine
US12000112B2 (en) 2018-10-24 2024-06-04 Volvo Construction Equipment Ab Method for controlling a hydraulic system of a working machine
WO2020216453A1 (fr) * 2019-04-26 2020-10-29 Volvo Construction Equipment Ab Système hydraulique et procédé permettant de commander un système hydraulique d'un engin de chantier
CN113767200A (zh) * 2019-04-26 2021-12-07 沃尔沃建筑设备公司 液压系统以及控制作业机械的液压系统的方法
CN113767200B (zh) * 2019-04-26 2023-03-31 沃尔沃建筑设备公司 液压系统以及控制作业机械的液压系统的方法
US11635095B2 (en) 2019-04-26 2023-04-25 Volvo Construction Equipment Ab Hydraulic system and a method for controlling a hydraulic system of a working machine
WO2022122934A1 (fr) * 2020-12-09 2022-06-16 Liebherr-Werk Biberach Gmbh Engin de levage et procédé pour régler la flèche d'un tel engin de levage

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